Haptic control device with a magnetorheological braking device

ABSTRACT

A haptic operating device having a magnetorheological braking device, a fixed holder, and two braking components. One braking component is non-rotatably connected to the fixed holder. Both braking components are continuously rotatable relative to one another about a rotation axis. A first braking component extends along a rotation axis and comprises a magnetically conductive core. The second braking component comprises a hollow casing part extending around the first braking component. At least one circumferential braking gap filled with a magnetorheological medium is between the first and second braking components. An electrical coil, surrounding the core and around the rotation axis, is between the casing part and the core. Two different radial braking gap portions and a disk contour are formed at a first braking gap portion between the casing part and the core, and a plurality of rolling bodies are arranged as magnetic field concentrators at the periphery of the core in a second braking gap portion.

The invention relates to a haptic operating device and in particular a haptic operating control button with a magnetorheological braking device with a fixed holder and with at least two braking components which can be rotated continuously relative to one another about an axis of rotation.

The haptic operating device or actuating device can be used in particular when operating technical equipment in motor vehicles and other vehicles, for example as a rotating knob, rotating knob/push button, for infotainment, air conditioning (temperature, ventilation level, distribution), as a gear selector switch, for navigation, with cruise control, with distance control, as seat adjustment, in the steering (steer by wire or steering in general) or in the steering wheel, in the handlebar or steering column of a two-wheeler, three-wheeler or four-wheeler (e.g., OFF-Highway vehicle such as vehicles from Polaris), jet skis, snowmobiles, ALL Terrain Vehicles, for adjusting the chassis, for changing the driving mode, for adjusting the windscreen wipers, for adjusting windows or for adjusting the sunroof, for parking assistants or for setting (partly) autonomous driving or even as a replacement steering wheel.

It can be used in motor vehicles, aircraft, airplanes, ships, boats, in agricultural engineering, for example in tractors or combine harvesters, harvesters and other field machines for agriculture. It can also be used in construction machinery and, for example, forklifts or similar machines or in medical or industrial systems.

The invention can also be used when operating or as an input device for washing machines, kitchen appliances and household appliances, radios, cameras and film cameras, hi-fi and television systems, smart devices, smart home devices, laptops, PCs, smartwatches, in a crown wheel of wristwatches or as a computer mouse or as a rotary wheel in a computer mouse, on game consoles, in gaming equipment, as rotary knob used in a keyboard or other devices.

Magnetorheological fluids have, for example, very fine ferromagnetic particles, such as carbonyl iron powder, distributed in an oil. In magnetorheological fluids, approximately round or spherical particles with a production-related diameter of 1 μm to 10 μm are used, with the particle size and particle shape not being uniform. If such a magnetorheological fluid is subjected to a magnetic field, the carbonyl iron particles of the magnetorheological fluid or the magnetorheological medium or the magnetorheological fluid link up along the magnetic field lines, so that the rheological properties of the magnetorheological medium are significantly influenced depending on the shape and strength of the magnetic field (transmissible shear stresses).

Brake units with magnetorheological fluids are known from the prior art, for example the MRF brake from Lord Corporation in various sizes (5 Nm, 12 Nm, 20 Nm): https://www.lord.com/products-and-solutions/steer-by-wire-tactile-feed back-device. These are also used, among other things, as “steer-by-wire tactile feedback”. These brakes function per se. However, a disadvantage of these MRF brakes is their relatively high basic friction (basic torque) in relation to the maximum torque (working range). The working range of the 5 Nm brake according to Lord's website/specification, it is 0.5 to 5 Nm (factor 10), with the 12 Nm brake the working range is between 1 Nm and 12 Nm (factor 12) and with the 20 Nm brake the working range is between 1 Nm and 20 Nm (factor 20). This relatively small working range is not sufficient for many applications, which is why these series products are primarily used for coarse motor applications (among other things, operation mostly with gloves, as in industry, on agricultural machines, on forklifts . . . ).

Fine motor applications such as operating infotainment systems with rotary/push controls using three fingers in the car, operating game consoles when gaming, but also steering a car require a significantly lower basic torque with a higher maximum torque at the same time, i.e., a significantly larger working range. The high basic torque, in particular, quickly leads to fatigue and makes very fine adjustments difficult to feel. However, the well-known MRF brakes do not allow a large working range because the friction surfaces are too large. Although smaller friction surfaces would reduce the basic torque, the maximum torque would also be smaller.

According to WO 2012/034697 A1 a magnetorheological transmission device has become known which has two components which can be coupled and whose coupling intensity can be influenced. A channel with a magnetorheological medium is provided to influence the coupling intensity. The magnetorheological medium in the channel is influenced by a magnetic field. Rotating bodies are provided in the channel, on which acute-angled areas containing the magnetorheological medium are provided. The channel, or at least part of it, can be subjected to the magnetic field of a magnetic field generating device in order to selectively (magnetically) concatenate the particles and to wedge them with the rotating bodies or to release them. This magnetorheological transmission device can also be used on a rotary knob to operate technical devices. Such a magnetorheological transmission device works and allows the transmission of very high forces or torques with a relatively small design or volume at the same time.

WO 2012/034697 A1 also discloses a rotary knob or operating knob in which the actual knob can be rotated about an attached shaft. The braking torque can be controlled via the magnetic field generated by an electric coil. If an even higher braking torque that can be generated is desired, cylindrical rollers can also be used instead of spherical rotating bodies, so that the magnetic field acts over a longer distance or larger area (there is a magnetic field concentration and wedge formation over a larger area). A haptic control device with such rotary bodies or rolling elements allows a satisfactory function and a very high torque for a haptic control knob, while at the same time there is a low braking/basic torque when the magnetic field is switched off (e.g., less than 0.5 Nm at a maximum torque of 50 Nm. The ratio of maximum generated torque to minimum torque (basic torque) is high (>100).

The disadvantage, however, is that the high maximum torque can only be achieved at low speeds of the haptic operating device. If the speed exceeds a value that depends on the respective design, the maximum torque drops considerably and does not always meet the requirements.

It is therefore the object of the present invention to provide a haptic operating device and in particular a haptic operating button with a magnetorheological braking or damping device, with which a low basic torque and a relatively high maximum torque can be generated at different speeds.

This object is achieved by a haptic operating device with the features of claim 1. Preferred developments of the invention are the subject matter of the dependent claims. Further advantages and features of the present invention result from the general description and from the description of the exemplary embodiments.

A haptic control device according to the invention can be used, in particular, as a haptic control knob or rotary knob or can be formed as a rotating element. The haptic operating device has at least one magnetorheological braking device with a stationary holder and with at least two braking components. One of the two brake components is non-rotatably connected to the holder. The two brake components are continuously rotatable relative to one another about a (common) axis of rotation. A first braking component extends along the axis of rotation (in the axial direction) and comprises at least one core made of a magnetically conductive material. The second brake component includes a hollow shell portion extending around the first brake component. At least one circumferential brake gap section or gap that is at least partially filled with a magnetorheological medium is formed between the first and the second brake component. At least one electrical coil wound around the axis of rotation and (radially) surrounding the core is accommodated between the casing part (shell portion) and the core. At least two (functionally) different and (preferably) radially and/or axially or obliquely formed brake gap sections are included or formed. A disk contour is formed between the casing part and the core at a first braking gap section. In a second braking gap section (formed between the shell part and the core), a plurality of rolling elements are arranged on the circumference of the core. The two braking gap sections are preferably formed at a common gap (braking gap). The two braking gap sections can also be formed on two spatially and/or structurally separate gaps (braking gaps).

The haptic operating device according to the invention has many advantages. A significant advantage of the haptic operating device according to the invention is that two functionally different brake gap sections are included, each configured in (preferably) a radial (and/or axial and/or oblique) direction. As a result, at different speeds of the haptic control device be braked in different ways. While one of the brake gap sections (functionally related) generates a higher torque at lower speeds, the other brake gap section, due to the different structure, also generates a relatively high torque at higher speeds. As a result, a constant maximum torque is achieved over the entire speed range, which is very advantageous in many applications.

The haptic operating device according to the invention has a simple structure, uses only a few parts and allows easy and inexpensive manufacture. The basic friction is low and a high maximum torque can be provided for different speeds and also at standstill. Production is simple and inexpensive.

The first braking component defines an axial direction. In particular, an axis of symmetry of the first braking component is the axis of rotation. The core of the first brake component preferably extends in the axial direction, but can also have a slight angle to the axial direction.

The invention makes it possible to generate a high braking torque at different speeds in a small installation space. The magnetic field passes through the two different braking gap sections between the core and the casing part, in each case essentially radially or in any case transversely to the axis of rotation.

The rolling elements serve, in particular, as magnetic field concentrators. Due to the rolling elements (serving as magnetic field concentrators) there can be acute angles between the individual magnetic field lines and the radial orientation, but generally or on average the magnetic field runs essentially radially. The same applies to the other brake gap section with the disk contour, in which a three-dimensional alignment of the magnetic field lines can also result at the radial end of the disk contour, but on average or overall are again aligned essentially radially.

In particular, in an axial area (directly) adjacent to the electrical coil, a disk contour or disk body is formed between the casing part and the core, and in a (different) axial section (directly) adjacent to the electrical coil, there is a plurality of rolling bodies (as magnetic field concentrators) arranged on the circumference of the core. In particular, the rolling elements are arranged in a common plane transversely or perpendicularly to the axis of rotation. Preferably, the rolling elements can move completely around the core. An outer surface of the core is preferably cylindrical in the second braking gap portion.

A radius or (typical or maximum) diameter of the first brake gap section is preferably approximately and in particular exactly the same size as a radius or (typical or maximum) diameter of the second brake gap section. This means that large torques can be generated even at higher speeds and when starting from a standstill.

The magnetorheological medium particularly wets the first and the second brake component at least in sections.

The (at least one) electrical coil is preferably wound around the axis of rotation and generates a magnetic field in an axial direction substantially within the core. The electrical coil is taken up radially between the core and the casing part. The electrical coil can be wound around the core or attached to the inside of the casing part.

The core consists of a magnetically (highly) conductive material. The first braking component comprises the core and in particular an axle or a shaft which, in particular, consists at least partially or completely of a magnetically non-conductive material. Preferably, the axle (the shaft) and the core are detachably connected to each other. The disk contour consists at least partially or completely of a magnetically (highly) conductive material.

In a preferred development, the disk contour is designed as a separate disk body. It is also possible that the disk contour is formed in one piece with the core and, e.g., T-shaped, with the long leg of the “T” running along the axis of rotation. It is also possible that part of the disk contour is designed in one piece with the core and is supplemented by a separate disk body. In simple and particularly preferred embodiments, the disk contour is formed by a separate disk body that is attached to or on the core.

The disk body is preferably applied to the core. For this purpose, the core has, in particular, an adapted receptacle. It is possible and preferred, for example, for the disk body to be connected or pressed onto the core. However, it is also possible for the disk contour or the disk body to be connected to the casing part and, for example, to be pressed into it. It is also conceivable that two disk bodies adapted to one another are used, between which a radial braking gap section is formed. A first hollow-cylindrical disk contour can be applied to the core and a second hollow-cylindrical disk contour with a correspondingly large inner diameter can be introduced into the casing part, so that the two disk contours are aligned with one another in the axial direction, for example, and leave a small (radial) gap between them. Between the two disk contours then remains a brake gap section which is, in particular, essentially radial in design.

In particularly preferred configurations, the disk contour has at least one disk pack. The pack of disks is formed, in particular, by a plurality of sheet metal disks that preferably lie directly against one another. Such a configuration enables, for example, the production of disk plates as a stamped part. Punched parts can be produced particularly easily and inexpensively in large numbers. If they are stacked on top of one another and, for example, pressed together, a disk package or a disk body with a significantly greater thickness can be provided easily and inexpensively. As a result, disk sheets (also called disks) and also disk packages can be produced very cost-effectively. Individual disks can also have different properties (e.g., due to different materials). Individual disks can also be made of (sintered) magnetic material (e.g., neodymium).

It is preferred that at least some sheet metal disks or almost all sheet metal disks or all sheet metal disks are each round and have the same diameter or at least similar diameters. However, it is also possible to use a few or individual non-round disk plates on which, for example, a non-round outer contour or a toothed structure or star contour is formed radially on the outside. If circular and non-circular disk sheets are stacked to form a disk pack, a complex outer contour can be created, which can locally lead to a greater magnetic field concentration. It is also possible for a disk pack to include a plurality of round (or non-round) disk sheets with different outside diameters. In this way, round sheet metal plates with a smaller and a larger diameter can be provided alternately.

In particularly preferred configurations, the disk contour has a cylindrical outer contour overall. It is also possible for the disk contour to be in the form of a star contour or to form one. A star contour as a disk contour can (preferably) have radially and/or (possibly) axially protruding magnetic field concentrators which are integrally connected to the disk contour or attached thereto. Then it is possible that a star contour is provided as a disk contour on a braking gap section. Rotating bodies are then included on the other braking gap section.

In particular, in such configurations, at least one star contour can be arranged as a disk contour on a braking gap section between the casing part and the core. This results in a variable gap height over the circumference of the braking gap section in the area of the star contour. In this configuration, too, the second brake gap section is preferably also an axially outer brake gap section.

Magnetic field concentrators are preferably formed or arranged on a star contour, which protrude (radially) into the gap, so that a circumferential braking gap section with variable gap height results in the area of the star contour.

The elements serving as magnetic field concentrators can protrude radially inwards or radially outwards or axially from a star contour. The magnetic field concentrators can, for example, be tooth-shaped, arc-shaped, sinusoidal, trapezoidal and can be arranged regularly or irregularly distributed and be of different heights.

A star contour can also be formed in the axial direction. This means that variable gap heights occur in the axial direction. As a result, the magnetic field can be concentrated in the axial direction at locations with smaller gap heights and reduced in the higher gaps. A mixture of “radial” and “axial” and/or oblique star contours is also conceivable.

It is possible and preferred for the disk contour to have an (axially) outwardly protruding outer contour on at least one axial side. The disk contour can be conical, bulbous, rounded or stepped overall. In particular, the disk contour is rotationally symmetrical formed area of the outer contour. The outwardly projecting outer contour can, for example, be supported on a cover or the like or be guided there. The outwardly protruding outer contour thereby makes it possible to provide a reservoir of magnetorheological particles.

In all configurations, it is preferred that a radial free space for a rolling body between the casing part and the core in the second brake gap section is greater than a gap height in the first brake gap section (in the area of the disk contour). A radial free space results from the difference in the gap height in the second brake gap section minus the diameter of the rolling element. The radial free space is typically divided approximately equally radially outside of the rolling body and radially inside of the rolling body. In simple cases, the rolling element is arranged radially centrally and the radial distance between the outer surface of the rolling element and the inner surface of the shell part and the radial distance from the outer peripheral surface of the core to the radially inner outer surface of the rolling element are approximately the same.

The radial free space (total) for a rolling body in the second brake gap section is preferably more than twice and in particular at least three times as large as the gap height in the first brake gap section. This means that in the normal case, the rolling element has more play radially outwards and radially inwards than the gap height on the disk body in the first braking gap section. It is also possible and preferred that the radial free space for a rolling body in the second brake gap section is four times or even greater than the gap height in the first brake gap section. A gap height at the braking gap section on the disk contour is preferably less than 0.15 mm and preferably less than 0.1 mm.

Preferably, the radial clearance in the second brake gap section and the gap height in the first brake gap section at the disk contour are (considerably) smaller than a radial distance in other areas of the gap. The radial distance from the outer diameter of the electrical coil or from the outer diameter of a coating over the electrical coil or an overmolding of the electrical coil to the radial inner wall of the casing part is (axially) outside of the two brake gap sections preferably (considerably) larger than in the two brake gap sections. The difference in size can reach and far exceed a factor of 2 or 3.

In specific configurations, the radial clearance for a rolling element in the second brake gap section is approximately 0.2 mm, while the gap height in the first brake gap section is approximately 0.05 mm. Deviations of +/−50% are possible in each case. Overall, the radial play on a haptic control button in the area of the rolling bodies is twice the radial free space, since rolling bodies are arranged on opposite sides of the core, a total of 0.4 mm in this example. In the area of the first brake gap section with a gap height of 0.05 mm, there is a total radial play of 2*0.05 mm, ie 0.1 mm.

Because of this very small amount of play, in many cases a separate bearing can be dispensed with, at least at the end of the haptic operating device with the disk contour. The disk contour then, together with the shell part, takes over the guidance or bearing of the shell part relative to the core. This enables an even simpler and more cost-effective construction.

In all configurations, the inner contour or preferably the casing part can be non-round (e.g., elliptical . . . ). The core can also be mounted eccentrically to the casing part. This results in a changing relative gap (section) during rotation.

In particularly preferred configurations, the first and second braking gap sections are formed on different axial sides of the electrical coil. Particularly preferable, at least one brake gap section axially borders, directly or indirectly, the electrical coil.

An axial width of the rolling bodies is preferably between half and twice the axial width of the disk contour. This allows a particularly effective transmission of the magnetic field in the braking gap section of the disk contour, which also enables a high magnetic field concentration at the second braking gap section in the area of the rolling elements. As a result, the braking effect in the first brake gap section and the second brake gap section is increased, while the overall axial length remains small.

A ratio of an axial width of the rolling bodies to an axial width of the electrical coil is preferably between 1:5 and 3:1 and in preferred configurations between 2:3 and 3:2.

A ratio of an axial width of the disk contour to an axial width of the electric coil is preferably between 1:5 and 3:2 and in preferred configurations between 2:3 and 3:2. Here, the axial width of the disk contour is understood to mean the width of the disk contour at the brake gap section. If the disk contour tapers radially outwards, for example, and the axial width of the disk contour decreases radially outwards, this is understood to mean the axial width of the disk contour in the vicinity of the radially outer end.

In all configurations, it is particularly preferred that the magnetic field of the magnetic circuit passes at least partly axially through the core and the casing part and to a considerable extent radially and particularly preferably essentially radially through the first and the second brake gap section. In simple configurations, the electrical coil is wound around the core and generates a magnetic field in the axial direction of the axis of rotation within the core, which is applied to the respective ends of the electric coil is passed radially outwards and passes at one axial end through the disk contour and the first brake gap section and at the other axial end through the second brake gap section and the rolling elements from the core to the casing part or vice versa. Such a configuration allows a particularly simple, inexpensive and yet effective construction.

Preferably, the rolling bodies consist at least partially and in particular almost completely or completely of a magnetically conductive material.

Magnetic non-conductive bodies or rolling elements can also be present. Non-conductive bodies can serve as placeholders or guide elements and can have any shape. Thus, magnetically non-conductive bodies can be arranged between the (magnetically conductive) rolling bodies. Several non-conductive bodies (e.g., guide elements) can be connected to one another, e.g., in the form of a cage. This makes assembly easier.

The disk contour particularly preferably guides the casing part in a rotatable manner and serves as a bearing point.

A closed chamber is preferably formed between the brake components. In particular, the closed chamber is at least to a significant extent and in particular essentially filled with a magnetorheological medium such as a magnetorheological fluid and/or e.g., (dry or powdered) carbonyl iron powder filled. In particular, the second brake component is rotatably received on the first brake component.

The first braking component preferably includes an axle formed at least in part from a non-magnetically conductive material. The core made of a magnetically conductive material is attached to the axle.

Preferably, the second braking component is axially displaceable taken on the first brake component. This can (also) serve, for example, to enable volume equalization in the event of temperature changes and/or in the event of a leak. It is preferred that a radial and/or axial position of the two brake components relative to one another is detected by sensors.

In all of the configurations, it is preferred that a click element is arranged at one and in particular at the distal end of the chamber. Such a click element allows in particular two states, after pressing the click element e.g., switches over a metal sheet in an audible and/or tactile manner and thereby performs a (small) axial displacement. Such e.g., designed as snap parts or snap disks click elements are known for example from keyboards or other devices and allow an inexpensive and effective tactile feedback when pressing a button or the like.

The click element is preferably arranged at one end of the chamber. An elastic membrane particularly preferably separates the chamber from the click element. The click element can be designed as a snap part or snap disk. This can provide volume compensation to the chamber as the axle continues to enter or exit the chamber.

In particularly preferred developments, the snap-action disk is designed such that a change in the clamped volume of the snap-action disk between the two states of the snap-action disk is adapted to a cross-sectional area of the axis multiplied by an axial offset of the snap-action disk when actuated. In particular, the two volumes differ by less than 50% or 25% and preferably by less than 10% or less than 5%. Such a configuration, in which the snap-action disk is adapted to the axis, ensures that only a small volume or possibly no volume at all has to be provided for volume compensation when the snap-action disk is actuated. The use of a click element or snap part at the distal end of the chamber in connection with the formation of the first braking gap section with the disk contour also close to the distal end of the chamber enables a particularly simple and effective guidance and mounting of the casing part, since only a small there is radial play and the disk contour can therefore (in many cases) assume sufficient guidance in the radial direction of the casing part.

In preferred developments, a sensor device or at least one sensor device for detecting a relative angle of rotation s between the core and the casing part is included.

A sensor device or at least one sensor device for detecting a relative axial position of the casing part in relation to the core is preferably included. Particularly preferably, the sensor device or at least one sensor device comprises at least one magnetic field sensor, which is designed to detect an angle of rotation s and an axial position. In particularly advantageous configurations, the sensor device comprises at least one Hall sensor.

In simple preferred configurations, the magnetic field sensor is accommodated on the stationary brake component and is exposed to a magnetic field acting in the radial direction. A rotation angle can also be determined via the orientation of the magnetic field sensor relative to the magnetic field. An axial displacement of the sensor device relative to the casing part can be derived from an intensity of the magnetic field strength.

A torque sensor can measure the torque.

The data recorded by the sensor device can be further processed by the electronics and also passed on to external devices. For example, a haptic operating device installed in a vehicle as a rotary knob/rotary pushbutton (in the steering wheel, in the center console, on the on-board computer, etc.), for controlling the radio and/or the navigation system, changing the chassis settings, etc., data about the change in angle in a vehicle can be transferred to the on-board computer/vehicle electronics/external electronics. Information about the condition of the roadway can be determined from this and/or the user behavior of the user can be recorded, evaluated and optimized. Artificial intelligence can then derive the user's wish from this and optimize/facilitate the control of devices.

At least one shielding device for at least partially shielding the sensor device from a magnetic field of the electrical coil is particularly preferred. The shielding device preferably comprises at least one shielding body. The shielding body is designed in particular to shield a magnetic ring unit for applying a defined (e.g., radial) magnetic field to the magnetic field sensor from interfering magnetic influences of the electric coil. For this purpose, the shielding body is preferably at least in sections of the magnetic ring unit. Preferably, the shielding device surrounds the magnetic ring unit on three sides, namely on both axial sides and radially outwards. The shielding device preferably comprises at least one separating unit arranged between the shielding body and the magnetic ring unit. This decouples the magnetic field of the magnetic ring unit from the shielding body. Furthermore, at least one magnetic decoupling device arranged between the shielding body and the casing part is preferably included. The separating unit and/or the decoupling device preferably have a magnetic conductivity that is many times lower than that of the shielding body. The shielding device and the magnetic ring unit are preferably arranged at a distance from one another.

A shielding device enables a significant improvement in the measurement quality. In particular, fine angular resolutions and small axial distances can be detected as a result. In all configurations, it is preferred that a rotary knob or a rotary wheel is formed on the casing part. The knob can be formed by a kind of coating.

At least one light source is preferably included for illuminating an at least partially transparent rotary knob.

A magnetic field strength of greater than 300 kA/m can preferably be achieved between the individual magnetically polarizable particles. In any case, if the electrical coil generates a maximum magnetic field or a magnetic field in the intended nominal range. The magnetic field strength (which can be generated) in the braking gap is preferably greater than 500 kA/m.

In all configurations it is preferred that at least one drive device is included for the active rotation of one of the brake components. As a result, not only can a braking torque be generated, but an active rotation can also be achieved, which means that extended haptic feedback can be given.

A device component according to the invention comprises a haptic operating device, as described above. It is also possible that two or more haptic operating devices are included. Such a device component can include a user interface, a control panel, a display, a touch-sensitive display with or without haptic feedback and/or at least one sensor or other input and output options.

In particular, the user interface can (also) be loaded by inductive coupling. Since the outer brake component, to which the rotary knob and thus also the user interface are attached in particular, can be rotated, cables for the electrical connection to the outer distal end cannot easily be routed up. Contacting via winding springs or sliding contacts is possible, but increases the basic torque and is therefore not particularly preferred. In the area of the LEDs or light sources, an electrical coil can be attached for an inductive coupling, which can be used both for energy transmission and for data transmission. In this way, the required electrical energy and the data for the display can be transmitted inductively to the user interface. Data coupling is also possible using other wireless methods.

The magnetic coil is preferably controlled mostly or predominantly during the operating time with a voltage of in particular 12V. In terms of haptics, it is (often) of considerable advantage if the braking torque of the magnetorheological braking device reaches the maximum or set value as quickly as possible. This is sometimes only possible with a greater voltage. A maximum braking torque is generally achieved by a maximum magnetic field in the braking gap. Since the magnetic field is generated by the current in the electrical coil (magnetic coil), the current must also be set to its maximum value as quickly as possible. In principle, you can always set the voltage to a high value, in this specific case instead of e.g., 12V to e.g., 24V. For this, however, all components (electrical coil or magnetic coil, the coil wire, etc.) would have to be designed differently (and e.g., a wire with a larger diameter would have to be used).

In preferred refinements and developments, a higher voltage (than would be necessary in continuous operation) is preferably set only at the beginning of a haptic feedback. In particular at the beginning or almost immediately after haptic feedback, a higher voltage is set (e.g., by a factor of 1.1 or 1.2 or 1.5 or 2 or 3 higher than would be necessary in continuous operation). The higher voltage is maintained until the current (or magnetic field) reaches the desired following value or maximum value (near, e.g., 90% or 95%) and/or the period is reached or exceeded, which the higher voltage can act. Thereafter, the voltage to the lower voltage of e.g., regulated back to 12 V. The system reacts more quickly and the desired braking torque is set more quickly. This achieves a closer approximation to a rectangle. An (approximately) stepped progression can be set.

In modern electric cars in particular, there are several voltages in the vehicle and high currents are possible, so that they do not have to be generated or transformed separately. Much higher voltages are also available in these electric vehicles (e.g. up to 800 volts) and such current strengths are possible that the properties described above can be used to advantage.

The applicant reserves the right to claim a method. Such a registration according to the method is used for haptic control of a device with at least one magnetorheological braking device. The magnetorheological braking device includes two (or more) braking components. The two brake components can be moved relative to one another. A first braking component includes a core made of a magnetically conductive material. At least one braking gap (gap) at least partially filled with a magnetorheological medium is formed between the first and the second braking component. At least one electrical coil applies a controlled magnetic field to the braking gap. In order to achieve a more rapid and in particular gradual change in the braking intensity, at least one performance parameter of at least one electrical coil is changed more strongly in a first period at the beginning of the change than would be permanently necessary to achieve the desired braking intensity.

Such a registration procedure is very advantageous. It allows better control of the braking effect. In particular, an improved step response can be achieved. (More gradual) stepped progressions of the braking effect are possible. As a result, the braking intensity can be more “rectangular” than with conventional control. Preferably, at least one performance parameter of the electrical coil is changed in the first period at least 10% or 20% or 30% or 50% or 100% more than the previous time than in the second period.

In particular, the second period is more than three or five times as long as the first period. The first time period preferably has a length of between 3 ms and 30 ms and in particular between 5 ms and 20 ms. In a specific embodiment, the first time period can be approximately 10 ms+/−5 ms.

In preferred developments, the current and/or the voltage of the electric coil are changed in order to change the braking intensity. The voltage is particularly preferably changed as a performance parameter.

Preferably, the power (the power parameter) of at least two electric coils is changed.

The braking gap can comprise at least two or three braking gap sections. More than two braking gaps can also be provided. In particular, at least two braking gap sections can be subjected to magnetic fields from different electrical coils.

It is possible and preferred that, in order to form a haptic stop or a tactile grid, performance parameters (at least one performance parameter, in particular the voltage) of at least one electric coil when there is an increase (compared to a previous point in time) is set higher for the first time period than for the second time period, which is contiguous to the first period and which is longer than the first period.

In preferred developments, the method with a carried out according to the application device, as disclosed in the context of this application. Therefore such a device can have the features described in all the claims in whole or in part. The method can be carried out with the features disclosed in the context of this application. A corresponding use is also possible.

The use according to the invention claims the use of a haptic operating device with a braking device in order to generate a high braking torque over a larger speed range, the braking device comprising at least two different radially designed braking gap sections. In a first braking gap section, a disk contour is formed between the casing part and the core in order to generate a high braking torque at higher speeds. In a second braking gap section, a plurality of rolling elements are arranged on the circumference of the core in order to generate a high braking torque at lower speeds. In particular, the design or development of a haptic operating device or a device component is used for use, as described above or disclosed in the context of the following exemplary embodiments.

In all of the configurations, the operating or actuating device can also be attached via a gear, belt (toothed belt/flat belt), linkage or otherwise superimposed or reduced, so that the actuation angle and the angle of rotation of the braking device connected thereto are different.

The haptic operating device or a haptic operating or actuating device can also be designed as a joystick device or joystick. A joystick device can also be attached via a gear, a belt (toothed belt/flat belt), a linkage or otherwise geared up or down, so that the actuation angle and the angle of rotation of the associated braking device are different. At least one drive device for actively rotating one of the brake components can be included in all developments and configurations of the haptic operating device or an operating or actuating device or a device equipped therewith. The control button, the control roller or the rotary unit can preferably be actively rotated. This allows more haptic information to be returned to the user.

Further advantages and features of the present invention result from the exemplary embodiments, which are explained below with reference to the accompanying figures.

show in it:

FIGS. 1 a-1 b show a schematic three-dimensional views of haptic operating devices with a magneto-rheological braking device's;

FIG. 2 shows a side view of a haptic operating device with a magnetorheological braking device;

FIGS. 3 a-3 c show different sections of haptic operating devices;

FIGS. 4 a-4 b show a highly schematic view of a sensor device and measurement results;

FIG. 5 shows a highly schematic view of a haptic operating device with a snap disk in different positions;

FIGS. 6-8 show further haptic operating devices in section;

FIG. 9 shows a highly schematic circuit for controlling the electrical coil; and

FIG. 10 shows torque curves of an electric motor and a magnetorheological braking device over the electrically introduced power;

FIG. 11 shows the resulting braking torque curves of a magnetorheological braking device for two different current strength curves over time; and

FIG. 12 shows a schematic view of a haptic operating or actuating device according to the invention with a drive device.

FIGS. 1 a and 1 b show two different haptic operating devices 100 according to the invention, each of which includes a magnetorheological braking device 1 and which can be used on different device components 200.

FIG. 1 a shows a haptic control knob 101 as a haptic control device 100. The control knob 101 is attached to the console 50 and can be mounted in a motor vehicle, for example. The operating button 101 is operated via the casing part 13 or a rotary part fitted thereon. A user interface 43 can also be used to transmit information.

In 1 b, the device component 200 is shown as a thumb roller 102 with a haptic operating device 100. The thumb roller 102 can preferably be used, for example, in steering wheels of motor vehicles or the like. However, the thumb roller is not limited to this use case. Depending on the installation situation, the thumb roller 102 can generally also be used with any other finger or with several fingers at the same time.

A haptic operating device 100 can be used, for example, to operate machines, medical devices, computer games, music terminals, input devices or for use in and for a motor vehicle. In a motor vehicle, the haptic operating device 100 can be used, for example, to operate air conditioning systems, radios, entertainment, navigation, the distance control, the driving assistant, the recuperation setting, to adjust the seats and to operate the infotainment. It can also be used on other devices or devices.

FIG. 2 shows a side view of a haptic operating device 100, which can be used as an operating button 101. The haptic operating device 100 includes a holder 4, which can be fastened to a console 50, for example, via a nut 51. The haptic operating device 100 includes a magnetorheological braking device 1 with two braking components 2, 3, of which the inner braking component 2 is not visible in FIG. 2 . The inner brake component 2 is connected to the holder 4. The holder 4 and the inner brake component 2 are designed to be stationary here. The other brake component 3 includes the casing part 13 and is rotatably accommodated on the first brake component 2.

The haptic operating device 100 has a compact design and inside the shielding device 75, which has a two-part shielding body 76 as a shielding housing, has a sensor device 70 (not visible here) for detecting the rotational position and the axial position of the casing part 13. The casing part is via pins 16 13 with a left cover 14 and a right lid 15 to seal an inner closed chamber 110.

Possible cross sections of a haptic operating device 100 according to the invention are shown in FIGS. 3 a to 3 c , e.g., shown in FIG. 2 . The haptic operating device 100 has a magnetorheological braking device 1. The braking component 2 is accommodated on the holder 4, which extends in the axial direction and to which the core 21 is fastened. The core 21 is surrounded radially by the casing part 13 as the outer or second brake component 3.

The magnetically conductive core 21 is of an electric coil 26, which is wound around the core 21. The electrical coil extends over an axial width 26 e. At the end of the core 21 facing the holder 4, a disk contour 41 is formed, which is applied here to the core and, e.g., is pressed. For this purpose, the disk contour 41 has a disk body 42 designed as a hollow cylinder. The receptacle on the core can also be non-round.

In particular, the core 21 can be made of sintered material (metal). The core can thus be manufactured more easily in the desired shape.

The disk body 42 consists here of a disk pack 44 which is formed by a plurality of thin disk plates 46. Here, the sheet metal disks 46 are each formed as a stamped part and can be stamped out, for example, from a magnetically conductive sheet metal with a thickness of 1 mm or 2 mm or even 3 mm. In this way, the required number of sheet metal panes can be punched out easily and inexpensively in order to produce the desired thickness of the pane body 42.

The individual disk plates 46 are pressed together and applied to the core 21 and thus, for example, screwed or pressed. A braking gap section 5 a remains in the area of the disk body 42 with a small gap height 41 b between the outer diameter of the disk contour 41 and the inner circumference of the casing part 13. The axial width 41 e of the disk contour 41 or its braking gap section 5 a is determined here by the number of disk laminations 46 and can be larger or smaller than shown.

Here, the disk contour 41 is axially directly adjacent to the electrical coil 26, which is accommodated in a coil holder 26 b and is completely sealed radially on the outside by a casting compound 28.

The disk body 42 is connected to the core 21 and the fixed brake component 2 and does not rotate during operation. This enables a hole or recess to be formed for the cable 45 to be fed through for the electrical connection of the electrical coil 26. The electrical coil 26 can thus be connected simply, inexpensively and quickly.

The disk contour 41 is formed here at the proximal end, that is to say at the end of the core 21 which faces the holder 4. At the distal end, that is, at the other end of the core 21, a braking gap portion 5 b is formed. The braking gap section 5 b extends over an axial width 11 e. There, the rolling elements 11 are distributed on the circumference of the core 21. The rolling elements 11 reinforce the magnetic field locally. The rolling bodies 11 can form a kind of magnetic field concentrators 80 for local amplification of the magnetic field when passing through the brake gap section 5 b.

A very high braking torque can be achieved by the braking gap section 5 b, in particular at low speeds of rotation of the casing part 13. A strong magnetic field can be transmitted from the core 21 to the casing part 13 through the braking gap section 5 a in the area of the disk contour 41, since the gap height 41 b is considerably less than the radial free space 11 c in the area of the braking gap section 5 b. As a result, a high torque can be generated, which is also made possible, in particular, at higher speeds. This means that a high torque can be made available over the entire speed range.

The axial width 11 e of the braking gap section 5 b and the width 41 e of the braking gap section 5 a are approximately the same here (+/−25%) and together are somewhat shorter than the electrical coil 26. A very compact structure is achieved overall.

The jacket part 13 is surrounded by a cover 49 as a rotary knob 23 in FIG. 3 a . The knob 23 is at least partially transparent so that it can be illuminated by the lighting means 18 in the form of LEDs, for example. The lighting can be controlled depending on the situation or independently of the situation.

At the front end, the closed chamber 110 inside the casing part 13 is closed off by a front cover 14 through which the brake component 2 is passed. A seal 38 is used for sealing. At the rear or distal end, the chamber 110 is initially delimited by an elastic membrane 31, which is adjoined on the outside by a click element 29 designed here as a snap-action disk.

By axial actuation of the knob 23, the snap disk or the click element is actuated and the jacket part 13 is moved slightly to the left overall. This axial movement can be controlled by the sensor device 70 with the magnetic field sensor 72 inside the holder or of the first brake component 2, which is surrounded radially by a magnetic ring unit 71. The magnetic field sensor 72 is designed in particular as a Hall sensor 72 and detects the alignment of the radial magnetic field relative to the magnetic field sensor 72. In this way, an angular position of the jacket part 13 relative to the core 21 can be detected. An axial adjustment of the casing part 13 by actuating the click element 29 leads to a relative axial offset between the magnetic ring unit 71 and the magnetic field sensor 72, which causes a change in intensity of the detected signal s. In this way, an actuation of the click element can be detected.

FIG. 3 b shows a slightly different representation of a haptic operating device 100 with a magnetorheological braking device, in which case, in contrast to FIG. the rotary knob 23 has been omitted.

A major difference between FIGS. 3 a and 3 b is that in FIG. 3 b , the first brake gap portion 5 a is provided with the disk contour 41 at the distal end of the casing part 13, while the second brake gap portion 5 b with the rotating bodies 11 is provided at the proximal end of the casing part 13.

In this configuration, for example, outside of chamber 110 between seal 38 and sensor device 70 there can also be a bearing for mounting jacket part 13 with respect to brake component 2. However, it is also possible here for the bearing to take place at one end only via the seal 38 and at the other distal end only via the disk contour 41.

Some magnetic field lines 8 are drawn in by way of example in FIG. 3 b . Furthermore, it can also be seen that in each case an (approximately) radial passage of the magnetic field lines 8 takes place in the braking gap sections 5 a and 5 b. A higher torque is generated in the brake gap section 5 a at higher speeds, while a higher torque is generated in the brake gap section 5 b at lower speeds.

The magnetic field sensor 72 is mounted on a sensor circuit board 79 and can be contacted via the contact pins 79 a. The electrical coil 26 is also supplied with current via this.

At least in the area of sensor device 70 and magnetic field sensor 72, inner braking component 2 is preferably made of a material that is not magnetically conductive or has little or no magnetic conductivity, in order to enable detection of the orientation and the intensity of the magnetic field of magnetic ring unit 71 in the interior of axle 12 or the to ensure first brake component 2. The sensor device 70 is accommodated there in a particularly protected manner (protection from water and dust).

In FIG. 3 b , an O-ring can be seen, which seals the cover 14 against the casing part 13.

FIG. 3 c shows basic schematic cross sections of braking gap sections 5 a and 5 b. In this case, on the left is braking gap section 5 b, wherein the core 21 can be seen inside, on which the rolling elements 11 are arranged schematically all around. The rolling bodies are in turn surrounded by the casing part 13. The rolling elements each have a diameter 11 d. A radial gap height 11 b is slightly larger than the diameter 11 d. A radial free space 11 c results as the difference between the gap height 11 b and the diameter 11 d. The radial free space 11 c is generally divided relatively evenly radially on the inside and radially on the outside.

A magnetorheological medium which comprises magnetorheological particles 19 is accommodated in the chamber 110. A gap 5 is provided in the chamber 110 between the brake components 2 and 3. The chamber 110 is at least partially filled with a magnetorheological medium 6 here. The medium here is preferably a magnetorheological fluid which, for example, comprises an oil as the carrier liquid, in which ferromagnetic particles 19 are present. Glycol, grease, water and viscous materials can also be used as a carrier medium, but are not limited to them. The carrier medium can also be gaseous or the carrier medium can be dispensed with (vacuum). In this case, only particles 19 that can be influenced by the magnetic field are filled into the chamber 110.

The ferromagnetic particles 19 are preferably carbonyl iron powder, with the size distribution of the particles depending on the specific application. A particle size distribution of between one and ten micrometers is specifically preferred, although larger particles of twenty, thirty, forty and fifty micrometers are also possible. Depending on the application, the particle size can also become significantly larger and even reach the millimeter range (particle balls). The particles can also have a special coating/shell (titanium coating, ceramic, carbon shell, etc.) so that they can better withstand the high pressure loads that occur depending on the application. The magnetorheological particles can account for this Application not only from carbonyl iron powder (pure iron), but e.g., can also be made of special iron (harder steel).

It is possible that only particles that can be influenced by the magnetic field are filled into the gap 5 or the chamber 110, with air or an inert gas being added if necessary. If, for example, only air or another gas is used, different solids can be mixed to improve certain properties. For example, graphite powder can be mixed in order to reduce the friction between the carbonyl iron particles since graphite exhibits a lubricating effect. In particular, the particles can be coated with PTFE. In particular, a coating with PTFE or a comparable coating prevents the particles from clumping together and forming larger heaps. Such larger heaps do not disintegrate easily or may not disintegrate at all. Alternatively, the disk bodies or roller bodies can be coated with PTFE to reduce friction. When using MRF without oil or other liquid as a carrier medium, it must be ensured that no water condenses in the brake chamber (MR space or MRF space). For example, silicic acid gel (known as silica gel) or another desiccant that absorbs water and thus removes moisture from its surroundings can be mixed in.

In all configurations, developments, and exemplary embodiments, powder without a carrier liquid can preferably be used. Then the use of up to about 80 percent by volume of carbonyl iron (iron powder) is possible, which greatly increases the braking torque if the remaining design parameters are adjusted accordingly (e.g., the field strength per particle should remain about the same as with a magnetorheological fluid (MRF), i.e., the field strength in the braking gap section or braking gap or active gap should be changed from, for example, LORD MRF 140 (40 percent by volume of carbonyl iron with, for example, oil as carrier liquid) to 80% carbonyl iron powder (without carrier liquid) can be twice as high. We are talking about magnetic field strengths in the gap of more than 200 kA/m up to values of up to 1,000 kA/m (1000000 A/m) or more. Another advantage of powder as a medium in the effective gap is that there is no sedimentation and no accumulation in the sense of “the iron particles in MR liquids are pulled in the direction of the magnetic field gradient (the force on magnetizable particles always acts in the direction of the stronger magnetic field, the carrier medium is displaced)” must occur in order to obtain such high particle concentrations. The maximum particle concentration is already present. This improves the reproducibility of the torques (a similar braking torque always occurs with the same current).

In all configurations, it is particularly preferred that the magnetically polarizable particles (especially when used as “dry” powder) (to a significant extent) include non-round particles (non-spherical particles) in which a ratio of the largest diameter to the largest transverse extension perpendicular thereto is greater than 1.25 or 1.5 It is also possible to form this ratio as a ratio of the greatest longitudinal extent to the greatest transverse extent, with the longitudinal and transverse extents in particular being measured perpendicular to one another.

The use of non-round particles is particularly advantageous since they enable an effective canting structure, since different non-round sections of the particles jam or wedge with one another.

Ratios of the largest diameter to the largest transverse extension perpendicular thereto of 1.75 or 2.0 or more are also possible and preferred.

Preferably, at least some of the magnetically polarizable particles are designed to move under the influence of the Magnetic field to jam or wedge together over a large area. This is possible, for example, with particles that are angular in sections or, for example, are triangular or polygonal overall or the like. Two (or more) correspondingly configured particles then jam together and can cause the particles to clump together very effectively and cause the two brake or clutch components to jam and brake together.

At least some of the magnetically polarizable particles are preferably designed to clamp or wedge together under the influence of the magnetic field at two or more locations spaced apart from one another. Such particles, which are non-circular, allow a very effective increase in the braking force or the braking torque, since, unlike spherical particles, they do not only touch at one point or in a small angular range, but at several points or even over an area.

Preferably, at least some of the magnetically polarizable particles have at least one trough section. Such an inwardly curved trough section allows particularly effective wedging with parts of other particles.

Preferably, at least one surface of at least one clutch or brake component adjoining the brake gap is designed to be non-smooth or (locally) uneven at least in sections. It is also possible that the particles or a significant part of the magnetically polarizable particles have elevations or elevations and/or depressions regularly or irregularly on the outer surface. As a result, canting with the particles can be reinforced. For example, at least one surface can have elevations and/or depressions in the manner of pointed or rounded dimples in golf balls. A surface with a pointed or rounded sawtooth profile is also possible. A relative level (at least some) of the Elevations or depressions is preferably at least 5% or 10% of the minimum diameter of a magnetically polarizable particle.

It has been found that a particularly effective canting and jamming of individual particles can be generated with high magnetic field strengths. For this purpose, a magnetic field strength of greater than 150 kiloamperes/meter (kA/m) or 250 kiloamperes/meter or 500 kA/m or more is preferably generated in the brake gap. In particular, a magnetic field strength greater than 500 kiloamperes/meter (kA/m) or 750 kiloamperes/meter or 1000 kA/m or more can be generated in the brake gap or is generated there.

If only powder is used without a liquid carrier medium, a different type of seal can be selected, thereby reducing the basic friction. The seal does not have to be pressed as hard against the surfaces, since it is not necessary to seal for liquids, only particles. A non-contact shaft seal such as a labyrinth seal can also be used, for example. This type of seal only rests on one of the two mutually rotating parts. In addition, the temperature dependence is reduced or almost eliminated. Liquid carrier media change their viscosity with changing temperatures, while carbonyl iron powder hardly changes its properties in very large temperature ranges (until the Curie temperature is reached). The temperature-related volume change is also negligible for powder, since the particles can redistribute among themselves if the volume of the individual particle changes.

The maximum volume fraction of carbonyl iron particles in powder form (approx. 74%) is also higher than in MRF with e.g., oil as a carrier medium.

The magnetorheological particles 19 chain together when a magnetic field is applied, as shown very schematically on the left in FIG. 3 c pictured. This creates a wedge effect, which leads to a significant increase in the braking torque at low and medium speeds.

For a more detailed explanation of this effect, reference is made to FIG. 4 of the applicant's international application WO 2018/215350 A1, which, with regard to the explanation of the effect, is fully included in the scope of disclosure of this application in an adapted manner.

A cross section through the braking gap section 5 a in the area of the disk contour 41 is shown on the right in FIG. 3 c . Radially on the outside between the outer contour of the disk contour 41 and the inner circumference of the casing part 13 there is a gap height 41 b which is considerably smaller and can be chosen to be considerably smaller than the radial free space 11 c in the brake gap section 5 b. The disk body 42 can be designed as a disk pack 44 and can include a plurality of disk metal sheets 46.

A rolling body 11 is shown in dashed lines in the right-hand part of FIG. 3 c , just as an example, in order to clarify the differences. It can be clearly seen that the disk body 42 allows a gap height 41 b with a smaller height. As a result, a strong braking torque and a high magnetic field strength can be achieved and transmitted there, which then also causes a correspondingly higher magnetic field strength and braking effect in the other brake gap section 5 b.

The sensor device 70 is shown in detail in FIG. 4 a . The first brake component 2 and the second brake component 3 embodied here as a casing part 13 are only indicated (dashed lines). The sensor device 70 is supported via the decoupling device 78 on the rotatable second brake component in a magnetically decoupled manner. The shielding device 75 consists here of three shielding bodies 76 from which the scattering of the magnetic field 8 of the electric coil 26 decrease. The shielding device 75 can also consist of only pot-shaped bodies or a pot-shaped body and a disk-shaped body which are connected to one another.

In addition, there is also a separation unit 77 for magnetic separation. The magnetic ring unit 71 is used to measure the orientation or the angle of rotation of the magnetorheological braking device 1. The magnetic field sensor 72 is arranged inside the first brake component 2, which is non-magnetic in this area. Small relative axial displacements, such as those caused by actuating a snap-action disk, can be used to detect the actuation of the control button 101, as shown in FIG. 4 b . The angle of rotation and the orientation of the magnetic field lines drawn in by arrows can be detected by the magnetic field sensor 72.

An axial displacement changes the received signal 68 of the sensor device 70 in accordance with the illustration in FIG. 4 b . FIG. 4 b shows the course of the amplitude 69 of the signal 68 detected by the magnetic field sensor 72 as a function of the axial displacement of the brake components 2, 3 relative to one another (push). The amplitude 69 of the detected signal 68 changes as a result of an axial displacement of the magnetic field sensor 72 in relation to the magnetic ring unit 71.

An axial displacement or pressing down (push) of an operating button 101 can be detected in this way. This preferably confirms a selection or position.

The angle of rotation can also be detected with the same sensor 72, the direction of the magnetic field 8 (arrows shown) being determined to detect the angle of rotation. The intensity determines the axial position. A change in the signal 68 can therefore be used to infer that a button or the snap disk 29 has been actuated. This is advantageous because a single (multidimensional) Hall sensor Determining the angular position and determining an axial position can be used.

FIG. 5 shows, very schematically, the haptic operating device with a snap-action disk 29 in two different positions, the unactuated position being illustrated on the left and the actuated position on the right. In the illustration on the left, the snap-action disk is curved outwards and downwards here and is guided here by the guide 29 a in the core (but not supported, so there is almost no friction).

The volume of the stretched triangle 29 b can be seen in the right half of FIG. 5 . The volume 29 b results approximately from the three-dimensional cone. If the haptic operating button 100 is actuated and the snap disk 29 is moved from the rest position (deflected) to a linear position within one plane, the casing part 13 is displaced axially downwards here in relation to the first brake component 2. As a result, an axial section 22 of the axis or emerges. of the first brake component 2 into the interior within the casing part 13. The change in volume 29 b of the snap disk 29 is preferably dimensioned in such a way that it essentially corresponds to the immersed volume of the first brake component 2. The immersed volume is calculated from the axial path 22 multiplied by the cross-sectional area of the first brake component 2 on the axle 12. By bringing surface 29 b as close as possible thereto, pressure buildup within chamber 110 can be minimized or prevented. Volume balancing can also be provided by a membrane 31 as previously discussed.

FIG. 6 shows a schematic cross section of a further haptic operating device, the first brake component 2 being fixed to a holder 4 with grub screws, for example. In this configuration, too, two braking gap sections 5 a, 5 b are provided, with a disk contour 41 being formed on the braking gap section 5 a and on the braking gap section 5 b rolling elements 11 or rotating bodies are accommodated on the circumference of the core 21. The rolling elements are guided over brackets 11 f.

Here, the disk contour 41 has an outwardly protruding outer contour 47 at the axially outer end, which is designed here, for example, as a cone, but can also be designed as a pin. As a result, a reservoir 32 for magnetorheological particles remains in each of the corner regions in order to ensure that the brake gap sections are adequately supplied with magnetorheological particles. In particular, carbonyl iron particles are attracted from the environment and concentrated in the magnetic field transition region.

Screws 48 are used to fill or empty chamber 110.

FIGS. 7 and 8 show two further exemplary embodiments of a haptic operating device, with the disk contour 41 being formed with the braking gap section 5 a at the distal end in both cases.

In FIG. 7 it can be seen schematically how a separate receiving ring for the rolling bodies 11 is fastened to the core 21 by a nut 40 b in the braking gap section 5 b.

FIG. 8 shows an exemplary embodiment in which both a separate receiving ring for the rolling bodies 11 and the disk pack 44 for the disk body 42 are fastened to the core 21 via nuts 40 b.

In FIG. 8 , a cover 14 is attached to the front end and a cover 15 is attached to the rear end.

The disk body 41 can be formed separately and in one piece or can also be formed as a disk assembly 44 with a plurality of disk plates 46.

Overall, a very inexpensive to produce haptic Operating device made available, whereby at least one bearing can be saved by a “bearing” via the disk contour 41, which also reduces the overall height. A very low basic friction is achieved. The fact that fewer parts are used makes production easier and more cost-effective. A smaller number of parts also improves the tolerance requirements, since tolerance chains are avoided. A haptic control knob, for example as a rotary knob or rotary element with a haptic control device, can be used in a wide variety of areas.

If necessary, an actuation can be detected via a snap part or a snap disk or a button or the like. The rotary knob can be illuminated, for example, via LEDs or the like. The body of the rotary knob can then be partially or completely milky in order to achieve a corresponding scattering effect.

FIG. 9 shows a schematic of a circuit for rapid activation of the electrical coil 26. The electrical coil 26 (magnetic coil) can be used here, for example B. be driven by an H circuit. This is only indicated here by switches. A voltage source 35 a used in normal operation or in continuous operation with a lower voltage of z. B. 12V (or 3V or 6V; depending on the application, a suitable voltage) provides the voltage for normal operation. For the voltage peaks, a voltage source 35 b with a higher voltage of, for example, 18V or 24V (or, for example, 6V or 12V) is connected via a switch. Then, the lower voltage power source 35 a is temporarily disconnected. After the maximum current has been reached, the higher voltage source 35 b is again disconnected from the circuit and the electrical coil 26 and the lower voltage source 35 a is reconnected. The switches can be any electrical components that are particularly capable of coupling and decoupling in the millisecond range. As a result, the current in the electrical coil 26 reaches the desired value more quickly. In a specific case, the desired current is reached within 10 ms instead of 40 ms. The change between the voltages can take place via an electrical circuit.

FIG. 10 shows a schematic representation of two braking torque curves generated, the braking torque generated (normalized and therefore dimensionless here—Y axis) being plotted against the electrically introduced power (normalized and therefore dimensionless here—X axis). The curve for a BLDC motor (“brushless direct current motor”) is shown on the left and the curve for a magnetorheological braking device is shown on the right. It can be seen that the electric motor requires significantly more power than the magnetorheological braking device for the same braking torque a braking torque of “14” requires the electric motor more than “130” normalized power, while the magnetorheological braking device requires a (significantly) lower power of less than “0.3”. The power consumption ratio is greater than 100:1 and is around 500:1 here.

Magnetorheological clutch devices and brakes have the advantage, among other things, that they require little power to engage or dampen movements, are quiet, generate little heat and react very quickly (˜ms), etc. The low power requirement is particularly advantageous for battery-operated components such as e.g., electric vehicles, in which the power consumption of all components is automatically reflected in the range of the vehicles. However, power consumption is also an issue in vehicles with combustion engines or electrical devices in general.

FIG. 11 shows the resulting braking torque curves of a magnetorheological braking device 1 for two different current strength curves (Y axis) over time (X axis). The dashed curve in the upper half of the figure represents the conventional course, in which the current intensity is increased directly to the desired current intensity. The voltage of the electrical coil 261 can also serve as a performance parameter. At the beginning, at the advance point in time 270, the braking torque is to be suddenly increased. For this purpose, the performance parameter 271 is significantly increased at the earlier point in time 270. In fact, it is increased more than is necessary to permanently achieve the braking torque that is then to be set. The performance parameter 271 is at least 10% or 20% higher than the second performance parameter 272. Here even much higher. It is clearly recognizable that the braking torque profile 265 reaches the desired value considerably more quickly due to the excessive increase. As a result, a better approximation of a box-shaped profile can be achieved.

Here, for example, at the point in time 0.1 seconds, the current strength is increased from 0 amperes to 2 amperes. The resulting course of the braking torque or the coupling intensity is shown in broken lines in the lower half of FIG. 11 in the dashed curve. The transmittable braking torque increases from the starting time at 0.1 seconds within about 25 milliseconds (time 0.125 seconds) to a read value of about 1.25 (normalized to e.g., an average value or a standard unit) and reaches after about 75 milliseconds (point in time 0.175 seconds) asymptotically (almost) the set limit value of about 1.5.

If, on the other hand, at the beginning of the clutch or the start of the braking or damping process, the current intensity is increased threefold to, for example, 6 amperes are increased here, as shown by the solid lines, the braking torque increases considerably more and reaches the final value of 1.5 after around 10 milliseconds. The “current boost” with increased current intensity is activated here for only about 10 ms. After that, as shown by the upper solid curve, the current intensity is reduced to 2 amperes. By briefly increasing the current intensity (“current boost”), a significant quicker setting (making available) of the clutch, damping or braking torque. This is very advantageous in several respects, as it allows you to stop quickly and experience a more direct haptic feeling (feedback). In reality, the difference between the two curves is very noticeable.

A combination of voltage and current is also possible. Voltages of over 24 volts and far above (e.g., >100 volts) are also possible.

Instead of one electrical coil, two or more electrical coils can be used, which are designed differently (wire thickness, number of turns, material . . . ) and are supplied with different currents in order to obtain the boost effect.

FIG. 12 shows a haptic operating device 100 according to the application for operating a wide variety of devices, facilities and devices, as described in this application and description (introduction, general description, description of the exemplary embodiments and claims). For turning, for example, a knob 23 (also in the form of a control roller) is used. The use of a steering unit or a steering wheel is also possible for operation. The rotary knob 23 or the control knob 101 can be connected in particular to the shaft 311 in a rotationally fixed manner.

The haptic operating device 100 can also be designed as a steer-by-wire steering system.

In this exemplary embodiment and in all other exemplary embodiments, refinements and developments, an actuator device 303 can be included in order to convert the rotational movement into another movement. In particular, the actuator device 303 can also only be electrically connected to the control knob 101.

The rotation of the control knob 101 is by means of a sensor device 70 and, for example, a rotation angle sensor detected. Depending on the angle of rotation, the actuator device 303 then controls other components or actuators.

A drive device 307 designed as an electric motor is connected to the shaft 311 here. The control knob 101 can be actively rotated by the drive device 307. As a result, the operating knob 101 is (actively) rotated in certain cases, for example—but not only—in the case of (simulation of) steering, in order to give the operator appropriate haptic feedback.

The movement of the operating button or rotatable operating element 101 can be braked in a targeted and controlled manner by means of a magnetorheological braking device 1. To control the braking device 1 and also the drive device 307 depending on various parameters and, e.g., the angle, a control unit 302 can be provided here. To this end, control unit 302 is operatively connected to sensor device 70.

Control unit 302 also takes data from an assistance system 304 into account, for example. As a result, the movement of rotatable operating element 101 can be influenced in a targeted manner depending on the driving situation. Control unit 102 can also be operatively connected to other sensors, not shown in detail here, in order to be able to specifically influence the behavior as a function of other parameters.

The braking device 1 is equipped here with a safety device 306 which removes a magnetorheological medium 6 (not visible here) from a gap 5 (also not visible here). In the event of a fault, for example, the braking torque can be canceled very quickly and reliably. The gap 5 and the medium 6 can be selected as described within the scope of this application and as shown in the further figures.

The operating or actuating device 100 according to the invention shown in FIG. 12 can be used to rotate an operating or actuating means of an operating or actuating unit that is not shown in detail here. The operating or actuating unit 101 is designed here as a rotatable button which is connected to a shaft 311 in a rotationally fixed manner.

The operating or actuating device 100 can also be embodied here as a steer-by-wire steering of a game (gaming; force feedback steering wheel), without being restricted thereto. An actuator device 303 is used for this purpose to convert the steering movement executed with the operating or actuating unit 101 into a (virtual) vehicle movement in a (racing) game (e.g., Need for Speed; Project Cars; Moto GP; Flight Simulator . . . ). For example, the actuator device 303 steers the (virtual) vehicle wheels or the vehicle wheel in the case of a motorcycle. The actuator device 303 is then only electrically connected to the steering unit 101.

The rotational movement of a steering unit is detected by means of a sensor device 70 and, for example, a rotational angle sensor. Depending on the angle of rotation, the actuator device 303 then steers, e.g., the vehicle wheels in the video game.

A drive device 307 designed as an electric motor is connected to the shaft (or steering shaft) 311 here. The steering unit 301 can be actively rotated by the drive device 307. As a result, the steering unit 301 is actively moved, for example when cornering or backing up, as would also be the case with a conventional mechanical steering system in a real vehicle.

The movement of the operating or actuating unit 101 can be braked in a targeted manner by means of a magnetorheological braking device 1. To control the braking device 1 and also the drive device 307 depending on various parameters and e.g., the steering angle is a (steering) control unit 302 is provided here. For this purpose, the (steering) control unit 302 is operatively connected to the sensor device 70. The (steering) control unit 302 also takes into account, for example, data from a (driving) assistance system 304 or data from other players or game situations (Sim Racer; racing simulators . . . ). As a result, the movement of the steering unit 301 can be influenced in a targeted manner depending on the driving situation. The (steering) control unit 102 can also be operatively connected to other sensors or information sources of a game, not shown in detail here, in order to be able to specifically influence the steering behavior as a function of other parameters.

The control button can also be used on or in an industrial plant, in computer peripherals, in automobiles, airplanes, etc. and can be supplemented by the active component described above.

The invention provides a haptic operating device that is compact, robust and very inexpensive. The haptic control device is particularly suitable for use in the automotive industry, but can also be used in all kinds of devices and machines.

A major advantage of the construction is that no cables, sensors or electronics are required on the outside. A high IP class is therefore possible in all configurations. In principle, everything is behind a mounting panel.

The electrical coil is preferably completely separated from the space containing the magnetorheological medium, in particular by means of a casting compound.

In preferred configurations, an axial displacement is possible, in which case, in particular, a liquid volume is displaced in the interior. Sufficient space is preferably provided between a cover and a disk contour so that the medium (or liquid) (carbonyl) therebetween is not compressed. (Otherwise this could lead to high axial displacement forces.) This provides an additional MRF reservoir from which particles can enter the area of the disk contour or the rolling elements can flow. Namely, magnetic particles always flow in the direction of the stronger field since magnetic particles are attracted by the magnetic field gradient.

The seal preferably runs on the axle. There is rotary movement (more than 100,000 revolutions are possible) and there can be linear movement for the probe. To ensure that the seal does not run in and form a running groove and that the friction is low, and the leakage (drag oil) does not become too high over the service life, a corresponding material pairing with a hard running surface is preferred.

As previously described, two rows with different magnetic field concentrators are used. The first brake gap section 5 a is equipped with a disk contour. The second braking gap section 5 b is equipped with rolling bodies and, in particular, rollers. Rolling elements and especially rollers with a round inner ring enable a high static moment. A disk contour enables good magnetic field transmission and high torque at high speeds.

The combined solution, also called hybrid solution, combines both advantages. In contrast, an axial transition of the magnetic field in the prior art had a smaller transition area and thus resulted in lower braking torques. In addition, an axial magnetic field transition has a smaller distance (radius) and therefore generates less moment. A brake gap section 5 a, which is also radial, with a disk contour has a larger diameter and thus generates a larger moment with the same force. In addition, the area is larger because the larger circumference spans a larger area. If the width of the contour disk is greater than ⅙ of the diameter, the braking torque that can be transmitted at the (circumferential) radial braking gap section is already greater than the maximum braking torque that can be transmitted on the axial surface! Finally, due to the lower gap height at the disk contour, the magnetic losses are smaller. All this also causes a higher braking torque at higher speeds.

Volume compensation for the push function can be provided by a membrane at the end of the jacket part. Behind the membrane is a click element like a snap-action disk (“Snap Dome”). This gives a haptic pressure point. You can also hear the click when the pressure point is reached, and the snap-action disk presses the entire button or the casing part back into the starting position back (similar to a mouse button on a computer mouse).

The membrane then seals off the MRF space. The volume behind the membrane acts as a volume balance when pressed. In the normal position, the snap disk has a bulge. If the button is moved in the axial direction, the stator of the braking device presses against the membrane and the snap-action disk. This will be pressed flat.

The design of the haptic control device can be enhanced by adding various light effects to the cover. A cost-effective variant is the use of a cap/cover with a transparent element, which is illuminated from below with LEDs. This can be done either by attaching a transparent sleeve to the shell part or by incorporating it into the cover, or by doing the entire inside of the cover as such (an inverted pot). For this purpose, the transparent part can be ground at an angle at the edges in order to deflect the light in the desired direction.

Normal glass can be used as the transparent material, or PMMA (acrylic glass). The advantage of PMMA is that you can use milky glass, which breaks the light inside and can thus illuminate the entire surface evenly. One or more LEDs can be used for lighting, also with different colors.

In all configurations, the outer brake component can also be designed to be non-rotatable and the inner brake component the be a rotatable component. In this case, the electric coil must be electrically contacted via lines through the outer braking component or e.g., via sliding contacts.

LIST OF REFERENCES

-   1 magnetorheological braking device -   2, 3 braking component -   4 holder -   5 braking gap -   5 a brake gap section for 41 -   5 b braking gap section for 11 -   6 magnetorheological medium -   8 magnetic field lines -   10 acute-angled area -   11 rolling body -   11 b radial gap height of 5 b -   11 c radial free space at 5 b -   11 d diameter of 11 -   11 e axial width of 11 -   11 f brackets -   12 axle -   13 casing part -   14 cover -   15 cover -   16 pin -   18 lights -   19 ferromagnetic particles -   20 axis of rotation, axial direction -   21 core -   22 axial path, axial section -   23 rotary knob -   26 coil -   26 b coil holder -   26 e axial width -   28 casting compound -   29 click element, snap disc -   29 a guide -   29 b volume -   31 membrane -   32 reservoir -   35 a power supply 12V -   35 b power supply 18V -   38 seal -   39 O-ring -   40 b nut -   41 disk contour -   41 b gap height of 5 a -   41 e axial width of 5 a -   42 disk body -   42 a holder -   43 user interface -   44 disk pack -   45 cables -   46 disk plates -   47 protruding outer contour -   48 screw -   49 cover -   50 console -   51 nut -   68 signal -   69 amplitude -   70 sensor device -   7 magnetic ring unit -   72 magnetic field sensor -   75 shielding device -   76 shielding body -   77 separation unit -   78 decoupling device -   79 sensor circuit board -   79 a contact pin -   80 magnetic field concentrator -   100 haptic control device, haptic operating device -   101 control button -   102 thumb roller -   110 closed chamber -   200 device component -   265 braking torque profile -   266 first performance parameters -   267 second performance parameter -   270 time -   271 first performance parameters -   272 second performance parameter -   302 control unit -   303 actuator device -   304 assistance system -   305 remanence device -   306 safety device -   307 drive device -   311 shaft 

1-32. (canceled)
 33. A haptic operating device comprising: a magnetorheological braking device having a fixed holder and at least two braking components, one of said at least two braking components being non-rotatably connected to said fixed holder, and said at least two braking components being continuously rotatable relative to each other about an axis of rotation; a first braking component of said at least two braking components extending along said axis of rotation, and a second braking component of said at least two braking components having a hollow casing part extending around said first braking component; at least one circumferential braking gap being formed between said first braking component and said second braking component, and said braking gap being at least partially filled with a magnetorheological medium; a core made of a magnetically conductive material, at least one electric coil being arranged between said casing part and said core, and said electric coil being wound around said axis of rotation and surrounding said core; and at least two different radial braking gap sections, a first braking gap section of said at least two different radial braking gap sections having a disk contour being formed between said casing part and said core, and a plurality of rolling bodies being arranged on a circumference of said core within a second braking gap section of said at least two different radial braking gap sections.
 34. The haptic operating device according to claim 33, wherein said disk contour is formed as a separate disk body or in one piece with said core.
 35. The haptic operating device according to claim 34, wherein said disk body is applied to said core and a core adapted holder.
 36. The haptic operating device according to claim 35, wherein said disk contour is connected to said core by one of pressing or screwing.
 37. The haptic operating device according to claim 33, wherein said disk contour is configured as a disk package having a plurality of disk plates.
 38. The haptic operating device according to claim 37, wherein at least one of said plurality of disk plates is designed as a stamped part.
 39. The haptic operating device according to claim 37, wherein said disk pack has disk plates which are configured to be essentially round and which are designed to be non-round.
 40. The haptic operating device according to claim 33, wherein said disk contour has an outwardly protruding outer contour on at least one axial side.
 41. The haptic operating device according to claim 33, further comprising: a radial free space configured for accommodating a rolling body being arranged between said casing part and said core in said second braking gap section; and said radial free space is greater than a gap height in said first braking gap section.
 42. The haptic operating device according to claim 41, wherein said radial free space for said rolling body in said second braking gap section is more than twice as large as said gap height in said first braking gap section.
 43. The haptic operating device according to claim 33, wherein said first and second braking gap section are formed on different axial sides of said electrical coil.
 44. The haptic operating device according to claim 33, wherein an axial width of said rolling bodies is between half and twice an axial width of said disk contour.
 45. The haptic operating device according to claim 33, wherein a ratio of an axial width of said rolling bodies to an axial width of said electric coil is between 1:5 and 3:2, and a ratio of an axial width of said disk contour to an axial width of said electrical coil is between 1:5 and 3:2.
 46. The haptic operating device according to claim 33, further comprising a magnetic field of said electrical coil that runs at least in part axially through said core and said casing part and radially through said first and said second braking gap section.
 47. The haptic operating device according to claim 33, wherein said disk contour rotatably guides said casing part and serves as a bearing point.
 48. The haptic operating device according to claim 33, wherein a gap height at said first braking gap section on said disk contour is less than 0.15 mm or less than 0.1 mm.
 49. The haptic operating device according to claim 33, further comprising a closed chamber being formed between said braking components, and said closed chamber being filled with a magnetorheological medium.
 50. The haptic operating device according to claim 33, wherein said second braking component is received on said first braking component in an axially displaceable manner.
 51. The haptic operating device according to claim 49, further comprising a click element being arranged at a distal end of said chamber.
 52. The haptic operating device according to claim 51, further comprising an elastic membrane separating said chamber from said click element.
 53. The haptic operating device according to claim 51, wherein said click element is designed as a snap disk, and a change in a spanned volume of said snap disk is adapted to a cross-sectional area of said axis multiplied by an axial offset of said snap disk upon actuation.
 54. The haptic operating device according to claim 33, further comprising a sensor configured for detecting a relative angle of rotation between said core and said casing part.
 55. The haptic operating device according to claim 33, further comprising a sensor configured for detecting a relative axial position of said casing part to said braking component.
 56. The haptic operating device according to claim 54, further comprising a shielding device configured for at least partially shielding said sensor from a magnetic field of said electrical coil.
 57. The haptic operating device according to claim 33, further comprising a light configured for illuminating an at least partially transparent rotary knob, and said light being accommodated on said casing part.
 58. The haptic operating device according to claim 49, wherein said magnetorheological medium has a multiplicity of individual magnetically polarizable particles, and a magnetic field strength between said individual magnetically polarizable particles is greater than 300 kA/m.
 59. The haptic operating device according to claim 33, wherein a magnetic field strength in said braking gap is greater than 500 kA/m.
 60. The haptic operating device according to claim 33, further comprising at least one drive device for active rotation of one of said braking components.
 61. The haptic operating device according to claim 33, configured as an operating button.
 62. A device component comprising a haptic operating device according to claim
 33. 63. The device component according to claim 62, further comprising: at least one user interface; a control panel; a display; a touch-sensitive display with or without haptic feedback; and/or at least one sensor. 